JP2018146046A - Clutch cylinder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch cylinder capable of efficiently discharging working oil in a cancel chamber without enlarging a centrifugal oil pressure origin diameter.SOLUTION: At a plurality of places along an inner periphery of a cancel plate 3, formed is an oil discharge port 18a configured to discharge working oil having been supplied to a cancel chamber 8 to the outside of the cancel chamber 8. The cancel plate 3 is regulated from moving in one side in an axial direction by a snap ring 6 fixed to a shaft part 11. In the oil discharge port 18, formed is an inclination surface 18b configured to enlarge a flow passage width B between the oil discharge port and an outer peripheral corner part 6a on a one-side surface of the snap ring 6.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a clutch cylinder used in, for example, an automatic transmission of an automobile.

  As shown in FIG. 5, a clutch cylinder 100 is incorporated in the power connection portion of the automatic transmission of the automobile. The clutch cylinder 100 is disposed so as to oppose an annular piston 110 that forms a hydraulic chamber 103 with the cylinder wall 102 of the casing 101, and is opposed to one side in the axial direction of the piston 110. 104, an annular cancel plate 112, and a return spring 113 interposed between the piston 110 and the cancel plate 112 in an elastically contracted state (see, for example, Patent Document 1).

The inner periphery of the piston 110 is inserted into the shaft portion 107 of the casing 101 so as to be movable in the axial direction.
The cancel plate 112 is provided with a seal lip 115 that seals between the outer periphery of an annular ring member 114 and the inner peripheral surface of the intermediate cylinder portion 110 a of the piston 110. The annular portion 114 is made of metal and is formed by press molding. The inner periphery of the cancel plate 112 is inserted into the shaft portion 107, and movement to one side in the axial direction is restricted by a C-shaped retaining ring 106 that is locked to the shaft portion 107.

In the clutch cylinder 100, when hydraulic oil is supplied from the oil supply port (not shown) to the hydraulic chamber 103, the piston 110 moves toward the cancel plate 112 against the urging force of the return spring 113, and the multi-plate clutch C is moved. Press to activate (connect) this.
When the hydraulic pressure in the hydraulic chamber 103 is released, the piston 110 moves in a direction away from the cancel plate 112 by the urging force of the return spring 113 and returns to the original position.

  Since the piston 110 and the cancel plate 112 are in rotation with the shaft 107, the hydraulic oil introduced into the hydraulic chamber 103 is pressed against the outer peripheral side of the hydraulic chamber 103 by centrifugal force. For this reason, hydraulic pressure (centrifugal oil pressure) due to centrifugal force is generated in the hydraulic oil. Since this centrifugal oil pressure hinders the return operation of the piston 110, the clutch disengagement operation cannot be performed smoothly. However, since the hydraulic oil introduced into the cancel chamber 104 generates a centrifugal hydraulic pressure (cancellation hydraulic pressure) that is substantially balanced with the centrifugal hydraulic pressure of the hydraulic oil in the hydraulic chamber 103, the return operation of the piston 110 is prevented from being hindered. be able to.

  By the way, in order to ensure good responsiveness when the multi-plate clutch C is connected, it is necessary to quickly discharge the hydraulic oil in the cancel chamber 104 discharged along with the movement of the piston 110 to the clutch chamber 109. is there. For this reason, notches 108 are formed at a plurality of locations on the inner periphery of the cancel plate 112, and hydraulic oil is discharged to the clutch chamber 109 through the notches 108 (see FIG. 6).

JP 2011-7278 A

However, since a part of the notch 108 is covered with the retaining ring 106 in a state where the cancel plate 112 is inserted into the shaft portion 107, the hydraulic oil in the cancel chamber 104 cannot be quickly discharged. For this reason, there exists a problem that the responsiveness of the multi-plate clutch C cannot fully be ensured.
Therefore, by increasing the length L in the radial direction of the notch 108, the hydraulic oil discharged from the cancel chamber 104 is moved over the outer periphery of the retaining ring 106 and discharged to the clutch chamber 109. .

Here, the centrifugal hydraulic pressure in the cancel chamber 104 is generated in the hydraulic oil existing in the radially outer space from the circumscribed circle A, starting from a virtual circumscribed circle A that is in contact with the radially outer end portion 108a of each notch 108. To do. For this reason, the longer the radial length L of the notch 108, the lower the centrifugal hydraulic pressure of the hydraulic oil in the cancel chamber 104. As a result, the difference between the centrifugal hydraulic pressure in the hydraulic chamber 103 and the centrifugal hydraulic pressure in the cancellation chamber 104 increases, the cancellation efficiency decreases, and the responsiveness of the multi-plate clutch C decreases. Therefore, there is a limit in increasing the radial length L of the notch 108.
In the following, the diameter of the circumscribed circle A, which is the starting point where the centrifugal hydraulic pressure is generated, is referred to as “centrifugal hydraulic starting point diameter”.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a clutch cylinder that can efficiently discharge the hydraulic oil in the cancel chamber without increasing the diameter of the starting point of the centrifugal hydraulic pressure.

  The clutch cylinder of the present invention forms an oil pressure chamber with the casing, and supplies hydraulic oil to the oil pressure chamber, thereby moving to one side in the axial direction to press the multi-plate clutch, An annular cancel plate which is disposed concentrically with the piston on one side in the axial direction of the piston and forms a cancel chamber with the piston, and provided in the cancel chamber, is attached in a direction to separate the piston and the cancel plate. The cancel plate is restricted from moving to one side in the axial direction by a retaining ring locked to the shaft portion in a state where the cancel plate is inserted into the shaft portion provided in the casing. The cancel plate has an annular portion extending radially outward from an inner peripheral surface thereof, and one side surface of the annular portion. The ring portion is configured as a contact surface that contacts one side surface of the retaining ring, and the annular portion discharges hydraulic oil supplied to the cancellation chamber to the outside of the cancellation chamber at a plurality of locations along the inner periphery thereof. The oil discharge port has an inclined surface on the inner wall on the contact surface side for expanding the flow path width between the retaining ring and the outer peripheral corner portion on the one side surface side. It is characterized by that.

  According to the clutch cylinder having the above-described configuration, the flow path width between the inner wall on the contact surface side of the oil discharge port and the outer peripheral corner portion of the retaining ring can be expanded by the inclined surface, so that the cancellation chamber The hydraulic oil can be efficiently discharged through the oil discharge port. In addition, since the inner wall portion on the back side of the contact surface of the oil discharge port becomes the starting point of the centrifugal oil pressure, the hydraulic oil can be discharged efficiently without increasing the diameter of the starting point of the centrifugal oil pressure.

In the clutch cylinder, the oil discharge port is a notch, and a non-inclined surface extending along the axial direction of the annular portion is formed on the back surface side of the contact surface of the inner bottom portion. The inclined surface may be formed continuously.
In this case, even when the centrifugal hydraulic starting point diameter and the outer diameter of the retaining ring are close to each other, the hydraulic oil can be efficiently discharged without increasing the centrifugal hydraulic starting point diameter.

Further, the oil discharge port is formed with a non-inclined surface extending along the axial direction of the annular portion on the back surface side of the contact surface, and the inclined surface is formed on the contact surface side. An intermediate surface extending radially outward from the inner periphery of the annular portion may be formed between the inclined surface and the inclined surface.
In this case, even when it is necessary to reduce the centrifugal hydraulic starting point diameter with respect to the outer diameter of the retaining ring, the hydraulic oil can be efficiently discharged without increasing the centrifugal hydraulic starting point diameter.

  In this case, the non-inclined surface may be constituted by a part of the inner periphery of the annular portion. In this case, since it is not necessary to form a non-inclined surface separately, the processing of the oil discharge port becomes easy.

  According to the present invention, since the hydraulic oil can be efficiently discharged without increasing the starting diameter of the centrifugal hydraulic pressure, it is possible to ensure good responsiveness of clutch operation.

It is principal part sectional drawing of the clutch cylinder which concerns on one Embodiment of this invention. It is a front view of a cancellation plate. It is principal part sectional drawing of the clutch cylinder which concerns on other embodiment. It is a front view of the cancellation plate which concerns on embodiment of FIG. It is principal part sectional drawing of the clutch cylinder which shows a prior art example. It is a front view of the cancellation plate of a prior art example.

Embodiments of the present invention will be described below with reference to the drawings.
In the following description, “radial direction” refers to the radial direction of the clutch cylinder, and “axial direction” refers to the axial direction of the clutch cylinder.
FIG. 1 is a cross-sectional view of an essential part showing an embodiment of a clutch cylinder according to the present invention.
As shown in the figure, in the casing 1 of the fluid automatic transmission, an annular piston 2 and an annular cancel plate 3 are arranged opposite to each other with a predetermined distance in the axial direction, and a return is provided between them. The spring 4 is interposed in an elastically contracted state. A multi-plate clutch 5 is accommodated in the casing 1 so as to face the outer peripheral side surface of the piston 2.

  The casing 1 includes a columnar shaft portion 11 extending toward one side in the axial direction (downward in FIG. 1), an end wall portion 12 extending radially outward from the base end portion of the shaft portion 11, and the end wall portion 12. And a cylindrical portion 13 extending from the outer peripheral end to the multi-plate clutch 5 side, and the cross section is substantially “U” -shaped at these portions.

  The inner peripheral surface 13 a of the cylindrical portion 13 and the outer peripheral surface 11 a of the shaft portion 11 are arranged to face each other in the radial direction, and a part of the space surrounded by these is configured as an annular hydraulic chamber 7. Further, an intermediate tube portion 12 a extending downward in the axial direction is formed in the middle portion of the end wall portion 12. Circumferential grooves 11b and 12b are recessed in the outer peripheral surface 11a of the shaft portion 11 and the outer peripheral surface of the intermediate cylinder portion 12a, respectively, and O-rings 14 and 15 are introduced therein. In addition, a C-shaped retaining ring 6 that restricts the cancel plate 3 from moving to one side in the axial direction is engaged with the shaft portion 11.

  The piston 2 is formed by pressing or turning a metal plate into a predetermined shape, and includes an annular main body portion 21a extending in the radial direction, an intermediate cylinder portion 21b extending in the axial direction from the outer periphery of the main body portion 21a, and a main body portion. A short cylindrical portion 21c extending in the axial direction from the inner periphery of 21a toward the cancel plate 3 side, and a pressing portion 21d extending further radially outward from the base portion of the intermediate cylindrical portion 21b and toward the multi-plate clutch 5 side.

The inner peripheral surface of the short cylinder portion 21 c is parallel to the axis of the piston 2, and the inner peripheral surface of the short cylinder portion 21 c is clearance-fitted to the outer peripheral surface 11 a of the shaft portion 11. Further, a space between the short cylinder portion 21c and the outer peripheral surface 11a of the shaft portion 11 is sealed by the O-ring 14 so that the piston 2 can move.
A base inner peripheral surface of the intermediate cylinder portion 21 b of the piston 2 is clearance-fitted to an outer peripheral surface of the intermediate cylinder portion 12 a formed on the end wall portion 12 of the casing 1. The intermediate cylinder portions 21b and 12a are sealed by the O-ring 15 so that the piston 2 can move.

The cancel plate 3 has a metal annular member 31 inserted into the shaft portion 11 concentrically with the piston 2 and an annular seal lip 32 attached to the outer peripheral surface of the annular member 31.
The annular member 31 faces the main body portion 21a of the piston 2 in the axial direction, and an annular cancel chamber 8 is formed therebetween. The annular member 31 is formed by press-molding a metal plate into a predetermined shape, and an annular portion 33 extending radially outward from the inner peripheral surface is formed on the inner peripheral portion thereof. In addition, arc-shaped protrusions 34 for restricting the diameter of the retaining ring 6 from being enlarged are formed at a plurality of locations of the annular portion 33 (see FIG. 2).

  The seal lip 32 is made of an elastic material such as rubber and is vulcanized and bonded to the annular member 31. The seal lip 32 is in contact with the inner peripheral surface of the intermediate cylinder portion 21b of the piston 2, and seals between the intermediate cylinder portion 21b and the annular member 31 in a state where the piston 2 can move in the axial direction. Further, one side surface (the lower surface in FIG. 1) of the annular portion 33 of the cancel plate 3 is configured as a contact surface 33b that contacts the retaining ring 6, and one side surface of the retaining ring 6 ( By making the upper surface in FIG. 1 abut, the cancel plate 3 is restricted from moving downward in the axial direction.

The hydraulic chamber 7 formed between the piston 2 and the end wall portion 12 of the casing 1 has an opening on the outer peripheral surface 11 a of the shaft portion 11 to supply hydraulic oil to the hydraulic chamber 7. An oil hole (not shown) for discharging the hydraulic oil from the hydraulic chamber 7 is communicated.
The return spring 4 urges the piston 2 in a direction to separate the cancel plate 3 from the cancel plate 3.

  With the above configuration, hydraulic oil is supplied to the hydraulic chamber 7 through the oil hole and the hydraulic pressure in the hydraulic chamber 7 is increased, so that the piston 2 resists the elastic force of the return spring 4 in one axial direction (in the figure). Move downward). At this time, the pressing portion 21d presses the multi-plate clutch 5 to transmit the driving force in the power connection portion. Further, when the hydraulic oil in the hydraulic chamber 7 is discharged from the oil hole and the hydraulic pressure in the hydraulic chamber 7 is lowered, the piston 2 moves to the other side in the axial direction (upward in the figure) by the elastic restoring force of the elastic member 4. , Away from the multi-plate clutch 5. Thereby, transmission of the driving force in the power connection portion is interrupted.

In the clutch cylinder having the above-described configuration, the annular portion 33 has the hydraulic oil supplied to the cancel chamber 8 at one side of the cancel plate 3 (at a lower side in FIG. 1) at a plurality of locations along the inner periphery. ) Is formed in the clutch chamber 9, which is a space of).
Each oil discharge port 18 is configured by a rectangular notch provided in the inner peripheral portion of the annular portion 33 (see FIG. 2), and an inner bottom portion (inner wall) 18a that is a portion facing the shaft portion 11 thereof. Are formed with an inclined surface 18b extending obliquely outward in the radial direction and a non-inclined surface 18c extending along the axial direction. The inclined surface 18b is provided on the contact surface 33b side which is one side surface of the annular portion 33, and the non-inclined surface 18c is connected to the inclined surface 18b on the other side surface 33c side of the annular portion 33. Is provided. In the case of the figure, the circumferential width H1 of the inclined surface 18b is smaller than the circumferential width H2 of the non-inclined surface 18c.

The inclined surface 18b is provided so as to oppose the outer peripheral corner 6a on one side of the retaining ring 6 (on the cancel plate 3 side). That is, the inclined surface 18b extends diagonally outward in the radial direction starting from a boundary portion with the non-inclined surface 18c while being separated from the outer peripheral corner portion 6a of the retaining ring 6 by a predetermined distance. By the inclined surface 18b, the flow path width B between the outer peripheral corner portion 6a of the retaining ring 6 and the inner bottom portion 18a on the contact surface 33b side of the oil discharge port 18 can be expanded.
The inclined surface 18b is formed simultaneously with the press molding of the annular member 31 of the cancel plate 3. For this reason, the inclined surface 18b can be easily formed without increasing the molding process of the annular member 31.

  The non-inclined surface 18c of each oil discharge port 18 is a portion serving as a starting point of centrifugal hydraulic pressure, and the diameter S1 of the inscribed circle S with which each non-inclined surface 18c contacts is a centrifugal hydraulic starting point diameter D. In order to ensure the responsiveness of the multi-plate clutch 5, the centrifugal hydraulic pressure starting diameter D is set to a value at which the centrifugal hydraulic pressure of the hydraulic oil in the hydraulic chamber 7 and the centrifugal hydraulic pressure of the hydraulic oil in the cancellation chamber 8 are substantially balanced. ing. In the present embodiment, the centrifugal hydraulic pressure starting point diameter D and the outer diameter D1 of the retaining ring 6 are close to each other.

  According to the clutch cylinder having the above configuration, the flow path width B between the oil discharge port 18 and the outer peripheral corner portion 6a of the retaining ring 6 is widened by the inclined surface 18b. The hydraulic oil in the cancel chamber 8 can be efficiently discharged through the oil discharge port 18 when the multi-plate clutch 5 is pressed. For this reason, although the centrifugal hydraulic pressure starting point diameter D and the outer diameter D1 of the retaining ring 6 are close to each other, the hydraulic oil can be efficiently discharged through the oil discharge port 18. For this reason, the responsiveness of the multi-plate clutch 5 can be ensured satisfactorily.

  FIG. 3 is a cross-sectional view of an essential part showing another embodiment of the clutch cylinder according to the present invention. This embodiment is different from the embodiment shown in FIG. 1 in the shape of the inner bottom portion 18 a of the oil discharge port 18. That is, in this embodiment, it is constituted by a part of the inner peripheral surface of the annular portion 33 on the other side surface 33c side that is the back surface side of the contact surface 33b of the annular portion 33, and along the axial direction. An extending non-inclined surface 18c is formed, an inclined surface 18b is formed on the abutting surface 33a side of the inner bottom portion 18a, and the inner portion of the annular portion 33 is interposed between the non-inclined surface 18c and the inclined surface 18b. An intermediate surface 18d is formed extending radially outward from the circumference.

The inclined surface 18b and the intermediate surface 18d are formed by recessing a part of the annular portion 33 in the thickness direction simultaneously with press molding of the annular member 31 of the cancel plate 3. For this reason, the inclined surface 18b and the intermediate surface 18d can be easily formed without increasing the number of molding steps of the annular member 31.
A gap X is formed between the non-inclined surface 18c and the shaft portion 11 to allow the hydraulic oil to flow.

In this embodiment, since the intermediate surface 18d is provided between the non-inclined surface 18c and the inclined surface 18b, the inclined surface 18b is arranged radially outward with respect to the non-inclined surface 18c. be able to. For this reason, although the non-inclined surface 18 c is close to the shaft portion 11, a flow path width B between the inclined surface 18 b and the outer peripheral corner portion 6 a of the retaining ring 6 can be ensured. Therefore, even when it is necessary to make the centrifugal hydraulic starting point diameter D smaller than the outer diameter D1 of the retaining ring 6, the hydraulic oil can be discharged efficiently and the responsiveness of the multi-plate clutch 5 can be ensured.
In addition, since the non-inclined surface 18c is constituted by a part of the inner periphery of the annular portion 33, it is not necessary to process the non-inclined surface 18c separately. Become.

  In addition, all the said embodiment is illustrations and is not restrictive. For example, the number of oil discharge ports 18 is appropriately increased or decreased according to the volume of the cancel chamber 8. In the embodiment shown in FIG. 3, the non-inclined surface 18 c may be formed radially outward from the inner periphery of the annular portion 33.

DESCRIPTION OF SYMBOLS 1 Casing 2 Piston 3 Cancel plate 4 Return spring 5 Multi-plate clutch 6 Retaining ring 6a Outer peripheral corner 7 Hydraulic chamber 8 Cancel chamber 9 Clutch chamber 11 Shaft portion 18 Oil drain port 18a Inner bottom (inner wall)
18b Inclined surface 18c Non-inclined surface 18d Intermediate surface 33 Ring portion 33b Abutting surface

Claims (4)

An annular piston that forms a hydraulic chamber with the casing and moves to one side in the axial direction to press the multi-plate clutch by supplying hydraulic oil to the hydraulic chamber;
An annular cancel plate disposed concentrically with the piston on one side in the axial direction of the piston and forming a cancel chamber with the piston;
A return spring that is provided in the cancel chamber and biases the piston and the cancel plate in a direction away from each other.
A clutch cylinder that is restricted from moving to one side in the axial direction by a retaining ring locked to the shaft portion in a state where the cancel plate is inserted into the shaft portion provided in the casing;
The cancel plate has an annular portion extending radially outward from an inner peripheral surface thereof, and one side surface of the annular portion is configured as a contact surface that contacts one side surface of the retaining ring,
The annular portion has oil discharge ports for discharging the hydraulic oil supplied to the cancellation chamber to the outside of the cancellation chamber at a plurality of locations along the inner periphery thereof.
The oil discharge port has an inclined surface on the inner wall on the abutting surface side, and has an inclined surface for widening a flow path width between the retaining ring and an outer peripheral corner on one side surface of the retaining ring.   The oil discharge port is a notch, and a non-inclined surface extending along the axial direction of the annular portion is formed on the back surface side of the abutting surface of the inner bottom portion, and the inclined surface continues to the non-inclined surface. The clutch cylinder according to claim 1, wherein a surface is formed.   A non-inclined surface extending along the axial direction of the annular portion is formed on the back surface side of the contact surface, and the inclined surface is formed on the contact surface side of the oil discharge port. 2. The clutch cylinder according to claim 1, wherein an intermediate surface extending radially outward from an inner periphery of the annular portion is formed between the inclined surface and the inclined surface.   The clutch cylinder according to claim 3, wherein the non-inclined surface is constituted by a part of the inner periphery of the annular portion.

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